Chucking machine



Dec. 14, 1937. G. o. GRIDLEY ET Al.

- CHUCKING MACHINE Original Filed July 16, 193] 4 Sheets-Sheet l ATTORNEYS Dec. 14, 1937- G. o. GRIDLEY ET Al.

CHUCKI NG MACHINE Original Filed July 16, 193] 4 Sheets-Sheet 2 www@ INVENTO R s GEORGE 0. @Av/@LEY 00A/11.0 H. Mo/vrGo/wfnr BEARL WHEELER ATTO R N EYS Dec. 1'4, 1937.

G. o. GRIDLEY ET A1. 2,102,412

GHUCKING MACHINE Original Filed July 16, 1.93] 4 Sheets-Sheet 3 INVENTORS 4afolc-IE QGR/DLEY 00A/ALD /f-MONTGDMERY EARL H. WHEELER M A ToRNEYs De 14, 1937 G. o. GRIDLEY ET AL 2,102,412

CHUCKING4 MACHINE original Filed July 16, 1931 4 sheets-sheet 4 GEORGE 0. R/DLE/ NHLD H. MONTGOMERY EARL 'v WHEELER ATTORNEYS Patented Dec. 14, 1937 UNITED STATES CHUCKING MACHINE George O. Gridley, New Britain, Donald H. Montgomery, Hartford, and Earl E. Wheeler, New Britain, Conn., assigner,- by meme aneignmenta, to The New Britain Machine Company, New Britain, Conn., a corporation of Connecticut Original application July 18, 1931, Serial N0.

551,136. ber 22, 1936.

Patent No. 2,055,435, dated Septem- Divided and this application May Z9, 1936, Serial No. 82,424. Renewed July 30,

15 Claims.

Our invention relates to a chucking machine and this application is a division of our application, Serial No. 551,136, flied July 16, 1931.

It is a general object of the invention to provide a machine of the character indicated, having improved chucking and clutching means interrelated and acting in a manner to make for high speed production, ease of operation, and safety.

It is `another object to provide in a chucking machine interrelated fluid pressure actuated clutching and chucking means under a single control.

It is another object to provide in a machine of the character indicated fluid pressure clutching and chucking means, together with means for assuring a proper sequence of chucking', clutching, unclutching. ami,- unchucking work pieces.

Another object is to provide improved fluid' pressure actuated chucking and/or clutching mechanism.

Other objects and various features of novelty and improvement will be hereinafter pointed out or will become apparent upon a reading of the specification.

'I'he invention in its preferred form is embodied in a multiple spindle chucking machine, only those parts necessary to an understanding of the invention of this application being shown herein. Other features, such as the frame, driving means, and other general features are disclosed fully in the aforesaid application of which this application is a. division and to which reference is hereby made for a lfuller disclosure of all features of the machine.

In the drawings which show, for illustrative purposes only, a preferred form of the invention- Fig. 1 is an axial rear end view of a chucking machine, partly broken away and parts shown in section and illustrating features of the invention;

Fig. 2 is a sectional view taken substantially in the plane of the line 2-2 of Fig. 1;

Fig. 3 is a sectional view taken substantially in the plane of the line 3-3 of Fig. 1;

Fig. 4 is a sectional view taken substantially in the plane of the line 4 4 of Fig. 3;

Fig. 5 is a sectional view taken substantially in the plane of the line 5-5 of Fig. 3;

Fig. 6 is a fragmentary top plan view inv partial section of clutch and 'chuck controlling means, also shown in part in Fig. 1;

Fig.- I `is a view in section of parts shown in Fig. 6 but seen from the side, the section being taken substantially in the plane of the line 1 1 of Fig. l;

Fig. 8 is a more or less diagrammatic or illustrative view of our improved uid pressure actuated chucking and clutching mechanism, together with fluid pressure generator and controls.

So much of the drawings of the aforesaid patent application as are necessary for an understanding of the present invention are included herein, but for a fuller description of the entire machine reference is made to the aforesaid application.

Each chucking spindle 250 may be supported in the indexible spindle carrier 98 in substantially the same manner and on anti-friction bearings as has been described inconnection with the screw machine disclosed in the parent application above identified, and the advantages there noted are, of course, inherent in a chucking machine as well as in the screw machine. In the form shown, and referring particularly to Fig. 2, it will be noted that the main spindle drive gear |82 drives a ring gear 25| rotatably carried on each spindle as by means of a double row bearing 252. The inner ring of the bearing is preferably rigidly carried directly on the spindle 250 while the outerring is rigidly carried in a recess or bore of the ring gear 25|. An advantage of an anti-friction bearing at this point is that when the spindle is unclutched from the drive gear and the drive gear continues to rotate, there is practically no tendency for the spindle to be dragged along with the drive gear, and stopping of the spindle is thus greatly facilitated. We have devised a most advantageous type of clutch device l by means of which thespindle'is positively driven and yetno difilculty is experienced in engaging the. positive clutch regardless of the normal speed of the driving portion thereof. Our improved clutch is disclosed in the present application merely by way of example as a satisfactory clutch for use in the present combination. In the embodiment of the invention herein-disclosed, we employ a positive type of bump or toothed clutch for positively driving the spindle during its normal and working rotation, and in order to permit such a desirable and positive type of clutch to be employed at the high speeds at which we desire to employ it, we provide a friction pick-up which initiates the rotation of the spindle and brings it to such a speed, that is, a speed approaching the speed ofthe driving portion of the positive clutch, that the positive clutch may be engaged without dimculty. In the forml illustrated, the ring gear 25| or any part which rotates therewith is provided with a driving clutch part 256, having positive clutch teeth 254 thereon. 'Ihe spindle carries a coact`\ ing clutch part, inthis case in the form of a sliding sleeve 255, having clutch teeth 256 to engage with the teeth 254. The sleeve 255 is spiined at 251 to what I-term an abutment sleeve 25|, which is itself splined at 256 to the spindle 2l6. The sleeve or spool 255 is* provided with a groove 266, so that the sleeve may be actuated by a fork part 26| (Figs. 1, 2), as will be later described. 'I'he abutment sleeve 256 is adjustably heldin desired longitudinal position on the spindle. by means of an adjusting nut device 262, so that it may be moved forwardly or rearwardly for purposes of adjustment, as will be described. pposite the inner end of the abutment sleeve 25 is a second abutment sleeve or collar 266, which may abut or form part of a friction clutch device 264 formed of plates. one or more of which may be carried by the ring gear, and one or more of which may be carried by the spindle or a part `rotatable therewith, so that when the abutment collar 266 is moved toward the right as viewed in Fig. 2, the friction clutch device will be engaged and the spindle will rotate with its driving ring gear 25|. In order to cause engagement or disengagement of the friction clutch device we employwedge members, such as balls 265, which may be carried in pockets or slots in the end of the abutment collar 266. The surfaces on the abutment collar `265 and on the abutment sleeve 256 are inclined to each other, in this case by beveling of! the edge of the abutment sleeve 256. Thus, it will be lseen that by moving the balls radially inwardly, the tendency will be to separate the abutment members 256-266, and since the abutment member 256 is rigidly held by the adjusting nut 262, the abutment collar 266 will be moved toward the right, to cause the friction clutch 264 to be engaged.

VThe positive clutch sleeve 255 is provided with a bell-,mouthed opening 266, so that when the clutch sleeve 255 is in its left-hand position as viewed in Fig. 2, the balls 265 may-move radially outwardly to permit disengagement of the friction clutch device 264.

Now, when the sleeve 255 is moved toward the right, the balls 265 will be moved radially inwardly by the tapered or bell-mouthed opening of the clutch sleeve 255, and thus the friction clutch device 264 will be engaged and the spindle 25|) will be rotated thereby. .Within the-sleeve 255 is a cylindrical opening 261 to maintain the balls in their radially inward position. When the spindle 250 has picked up speed, whether it bethe same speed as the drive gear 25| or slightly less, the positive clutch sleeve 255 may be moved farther towards the right, so as to cause the enlargement 266 in the clutch sleeve opening or counterbore to be positioned over the balls, and the balls are thus permitted to move radially outwardly and to disengage the friction clutch device 264. Further movement of the positive clutch sleeve 255 will cause the positive clutch teeth 254-256 to be engaged with eachother, and since the friction clutch device has already initiated the rotative movement of the spindle 255, there will be no dimculty incausing the positive clutch teeth which are now rotating to engage with each other without clashing or grinding of teeth. When it is desired to stop the spindle, the clutch sleeve 255 is merely moved toward the left, which action first causes `the positiv clutch teeth to become disengaged and which incidentally in 'the form shown causes the friction clutch device to be engaged and immediately thereafter causes the friction clutch means to be disengaged by the radially outward movement of the balls 265 when they enter the tapering or bell-mouthed 'opening of the sleeve.

Adjustment of the friction clutch pick-up means is readily eected by turning up the adjusting nut 252 so as to bring the two abutment sleeves closer together. Wear in the friction clutch device is thus compensated for. It will be seen that by means of our improved clutch device the spindles may be rotated at exceedingly high rates of speed and by a positive clutch. 'I'he friction clutch portion of our device acts only as a spindle speed pick-up device and does not, in the preferred form, drive the spindle at times when work carried by the spindle is being acted upon by the tools. At such times, the spindle is being driven by the positive clutch with all the attendant advantages of such a clutch.

It might be here stated that in the preferred form each spindle clutch is provided with its independent fork device 26| (Fig. 1) which may be slidably mounted upon the studs 221 described in the aforesaid application and employed in the screw machine for supporting the chucking slide. Each fork device 26| is also provided with a finger 269 which may be engaged with a track or slide shoe portion 210 (Figs. 1, 6), which is fluid pressure actuated as will be later described. Each fork 26|, or, rather, the finger portion 269 thereof of each spindle in other than the chucking position, may be engaged and held against endwise unchucking movement by a track ring 21| 'on the frame.

The chucks of the chucking machine are uid pressure actuated. 'I'he chucks may be of any desired type, and we have illustrated (Fig. 2) a rather well-known type of two-jaw chuck which is actuated to close the same by a rearward movement of the draw rod and to be opened by a forward movement thereof.

In the preferred form we employ a cylinder and piston for each chuck, and the cylinders are preferably so arranged as to be non-rotatable even though the spindles themselves are rotatable at high speed. A rear portion of each spindle may be provided with an dditional anti-friction bearing 216, and at the eratreme rearend of the spindle is an anti-friction bearing 214, which supports the non-rotatable cylinder unit 215 of desired form. The cylinder unit 215 is provided with fluid pressure inlet and. outlet ports or passages 216-211 at opposite sides of the piston 216. The piston has projecting gudgeons 216-260, which project respectively at the rear and forward ends of the cylinder and which may fit relatively tightly. Stufilng boxes may, if desired, be provided, but, generally speaking, a relatively tight t will serve to retain the pressure fluid in the cylinder, and if oil, for example, is the pressure fluid, a slight leakage of oil is rather advantageous for lubricating various bearings and parts adjacent to the leaks. Mounted on the piston gudgeon 219 is an anti-friction bearing 26 'which supports a frame or yoke device 262, which is rigidly but adjustably secured to the rear end of the draw rod 2 12, as by means of a screw threaded connection and a lock nut 263. It will be seen that, with the cylinder 215 held stationary, the spindle 250 may rotate relatively thereto by reason of the bearing 214. Likewise, the draw rod 212, by reason of the.

bearing 28|, may rotate relatively to the piston. The piston 218 may rotate to some extent in the cylinder, but under normal conditions the principal rotation will-be between the draw rod 212 and the piston. l

For the purpose of actuating the spindle clutch through the fork device 26| and the shoe or track actuator 210 weemploy a uid pressure piston and cylinder. may be in the form of a -bracket device slidably mounted upon the rods 2|1 and 2|8 on the frame of the machine. A piston rod 284 may be adjustably secured to the bracket 210 and be actuated by a fluid pressure piston 285 in a cylinder 286, fixed on the frame or rods 2|1-2I8, to be described more in detail. The ilow of fluid pressure to opposite ends of the cylinder 286 is controlled by a piston valve 281 in a valve casing 288,

which piston valve may be manually actuated through its rod 289, link 290 and crank 29| on shaft 292, which may be manually rocked by a handle at any convenient position on the machine:

The fluid pressure connections and the flow of fluid may be traced best by reference to the diagrammatic showing of Fig. 8. In the present embodiment the device is arranged so that all of the chucking cylinders in positions other than the loading position are maintained in chuck-closing position by direct pump pressure, while the cylinder of the spindle in loading position is initially actuated by uid from an accumulator, thepressure on the actuated piston being thereafter maintained constant by the pump after the accumulator pressure has caused it to operate. In the form shown we employ a pump, such as a gear or other positive type pump, 293, one branch 294 of the discharge side of which communicates with a passage 295 in the accumulator valve housing. A spring pressed valve 296 acts as a pressure regulat-ing valve, to permit the entry of high pressure fluid from the line 294 into the accumulator bell 291. The setting of the Valve 296 determines the limit below which the pump discharge pressure may not fall during normal operation. A differential relief valve 298 is provided which is forced to the position indicated in Fig. 8 by the pump pressure iluid. When the accumulator is charged, the pressure of the accumulator iiuid shifts the valve 298 to uncover the relief passage 299 to discharge excess fluid from the accumulator. When the system is shut down the pump of course ceases to furnish pressure iluid and the spring pressed Valve 296 is moved to the extreme left as viewed in Fig. 8 so as to permit the accumulator to drain through the dotted line port of the valve 296 and the drain pipe communicating with the spring chamber of the valve. During normal operation the pump pressure maintains the valve 296 in a right hand position to blank oi the dotted line port therein.

We may employ a valve 300 urged upwardly by a spring 302. This valve normally closes the discharge from the accumulator, and pump pressure iiuid may flow through port 30|, beneath the valve skirt, and through ports in skirt to cylinder line 303 to maintain the piston 218 in chucking position in its extreme position. When the chucking lever is actuated to shift the valve 281 as above described, there will be a quick ilow of pump fluid through cylinder line 303, port 304, etc., thus momentarily reducing the pump pressure below the valve 300, and the accumulator. pressure, being momentarily greater, will `shift the valve 300 to cause the skirt of the valve to cut oi the port 30| to thus maintain pump: pressure on the The track actuator 210' cylinders in working positions` (through line 300) and the accumulator will discharge through cylinder line 303 to shift the piston 218 in` loading station.v When the pressure in the accumulator drops, the spring 302 moves-the valve 300 to again close the accumulator discharge to line 303 and again permit direct pump pressure to enter cylinder line 303 to either complete movement of the piston 218 in-chucking position, or, if its movement is completed, to maintain the sam'e under static pump pressure. Thus the large volume of accumulator pressure fluid is available for shifting the chucking piston in loading position and direct pump pressure is available for completing the piston shifting and maintaining the same under static pump pressure. An operation may then be performed on a work piece chucked in loading position.

'Ihe other branch 305 from the discharge side of the pump communicates with an inlet passage 306 in the distributor sleeve 301, which is secured to the frame. Within the sleeve and normally in iixed rotative position is a distributor plug 308, and an annular passage 309 is provided, preferably in the'plug itself, so that there is a constant communication between the pump inlet passage 306 and such annular passage. Communicating with the annular passage 309 is a ,longitudinal passage 3|0 in the plug which communicates at the forward end of the latter through a side outlet 3H with an interrupted annular groove passage 3|2 in the plug. The groove 3|2 extends circumferentially about three-quarters of the way around the'plug.

'I'he spindle carrier itself or some part indexible with the chucking cylinders 215 carries a sleeve 3|3, fitting but indexible with the cylinders about thenormally fixed plug 308.- The sleeve 3|3 in the plane of the line 5-5 (Fig. 3) is provided with four outlet passages 3|4, 3|5, 3|6, 3|1, each of which passages is connected, as by means of a pipe 3|8, 3|9, 320, 32|, respectively, with the tail end of the chucking cylinders 215. Pressure exerted on said tail end serves to draw each draw-rod 212 in the chucking direction. Thus it will be seen that with the plug 308 and sleeve 3|3 in the position shown in Fig. 5, the tail ends of three of the cylinders will be in communication with the interrupted annular groove 3|2. and consequently in communication with the longitudinal passage 3|0, annular groove 309 in the plug, inlet passage 306-in the frame sleeve 301, and the discharge side 305 of the pump. Consequently, the three chucks in the positions other than loading position will be constantly held closed by high pressure fluid directly from the discharge side of the pump.

The distributor sleeve 3|3 is provided in the plane of the line 4-4 (Fig. 3) with passages 322, 323, 324 and 325, which are in communication, respectively, through pipes 326, 321, 328 and 329 with the head ends of all of the chucking cylinders. The plug 308 is provided in the plane of the line 4-4 of Fig. 3 with an interrupted annular groove 330, with which the passages 323, 324, 325 are in open communication, as shown in Fig. 4, so that the head ends of each of the cylinders, other than the one in the loading position, are in open communication with such interrupted annular groove. Communicating with that groove 330 is a longitudinal passage 33|, which communicates with an exhaust opening 332` (Figs. 3, 8), for example, with the space between the two sleeves on the plug. Thus, the

head end of each of the cylinders, other than the '15 The plug su is provided wima longitudinal passage 333 in constant communication with anannular ygroove 334 in the plug. Passage 333 is in 'communication at one end through a plug radial' passage 335 (Fig. 5) with'the port or passage 3|.1 communicating through the pipe 32| with the tail end of the cylinder in loading position. The plug 303 is provided with another longitudinal passage 338, which communicates with an annular groove 331 in the plug, and at its opposite end communicates throughs radial passage 322 (Fig. 4)-, pipe conection 322 in sleeve 3|3, and through pipe 328 with the head 'end of the cylinder in loading position, that is, the upper cylinder in Fig. 8.

Ihe annular plug passage 334 which, as stated, communicates with the tail end of the cylinder in loading position, is connected through pipe connection 338 and pipe 333 with the top pipe connection 340 in theA clutch cylinder 286.

The annular plug passage 331 which, as stated, is' in communication with the head end of the cylinder in loading position, communicates through the pipe connection 34| and pipe 342 with an end passage 343 in the control valve casing 283.

The operation'is as follows:

With the parts in substantially the `position shown in the drawings, and referring particularly to Figs. 3 to 8, it will be seen that the three chucks in working position are closed and held closed by high pressure fluid directly from the discharge side of the pump. The fluid pressure actuated spindle clutches heretofore described are likewise closed, so that the three spindles in working positions will be rotating with the chucks closed and held closed by direct pump pressure. The spindle in loading position, that is, the upper position in Fig.'8, has the spindle drive clutch thrown out, so that the spindle is stationary, and the chucking piston is in its forward position, so that the chuck is open. The control valve handle has been thrown over to the right to the position indicated as "1st (Fig. 8).

It may then be seen that the spindle clutch has been thrown out by accumulator pressure fluid which has passed from the accumulator through pipe 303, pipe connection 304, into the annular space between' the ends of the spool valve 281, and then through the passage 344 and into the tail end of the cylinder 288, thus maintaining the spindle clutch piston 285 in the left-hand position as viewed in Figs. 7 and 8.` At the same time the tail end of the chuck cylinder in loading position will be in communication through the pipe 32|, e 3|1 (Fig. 5). passages 335 and 333, annular passage 334, pipe connection 338, pipe 333 and pipe connection 340 in the clutch cylinder.288, the annular piston groove 345 in the clutch piston 285, and through thepassage 348 in the control valve cylinder, with the exhaust passage 341.

Pressure fluid is free to flow from the space between'the pistons of the control valve through port 343, pipe 342, pipe connection 34| and longitudinal plug passage 338, passage 322 (Figl'4), pipe connection 322 and pipe connection 328 to the head end of the cylindervin loading position, and thus cause the chucking piston ofthe cylinder in loading position to remain forward and the chuck openlw' l f Av newpiece of work maynow befinserted in the chuck. -The manual valve control handle lis then shifted to the'positlon indicated- 2nd i!!l Fig. 8, which moves the end 349 of spool valve `exhaust passage 341, and pressure iluid may pass through pipe 303,.pipe connection 304, passage 348, annular passage 345, pipe connection 340 and pipe 333, and eventually to the tail end of the cylinder in loading position, so as to-close the chuck. The spindle will still be unclutched but the work will now be chucked.

In order to close the spindle clutch the manual control valve handle is thrown toward the left to the position indicated "3rd in Fig. 8. 'Ihis movement will place the control valve 281 in the extreme left-hand position. It will be seen that pressure iluid through the pipe 303 and central connection 304 may still pass momentarily through passages 348, 345 to pipe 339, to the tail end of the cylinder in loading position, so as to maintain the work chucked. but at the same time the tail end of the cylinder 288 is in communication through the passage 344 and to the right of the right-hand piston 35| o f the control valve with the exhaust passage 341 and the head end space 352 of the clutch cylinder 288 will then be in communicationwith the source of pressure between the two heads of the piston valve, and the clutch piston 285 will be moved toward the right.,

so as to throw the spindle clutch in, and the spindle rotation will then be started. After the shift of the clutch piston 285 to the right to close;v the clutch pressure fluid may still reach the tail end of chucking cylinder in loading position by passing by the head end of cylinder 288 and through pipe 333, etc., to maintain that chuck closed.

After the turret or spindle carrier has indexed, another spindle will then arrive in loading position, and it will be in the same condition that the spindle which just left the loading position was in, that is to say, the spindle will be rotating and the rwork will be chucked. 'I'he manual control valve handle is then shifted to the right, back to the position indicated 2nd. Then, through the pipe connections heretofore described, the tall end of the clutch vcylinder 288 will be put in communication with pressure fluid and the head end 352 of that cylinder will be put in communication with the exhaust, so that the clutch piston 285 will be shifted toward the left and will again occupy the position shown'in Figs. '7 and 8, and the spindle clutch will be thrown out but the work will still be clutched. 'Ihe manual control valve handle would then be shifted farther toward the right, to the position designated lst, which is the position in which the' parts arein Figs. 7 and 8. This further shifting of the control valve to its extreme right hand position will still permit pressure fluid to maintain the clutch piston 285 in its left hand position, so as to maintain the clutch open, but

through the pipe connections heretofore described the tail end of the cylinder in chucking position will be opened to the atmosphere, and

the head end will be opened to accumulator pressure, to open the chuck, so as to discharge the nished work piece and permit the insertion of a new work piece.

. Thus briefly, with the parts in the position shown in Figs. 7 and 8, the first shift of the manual control handle to the 2nd or intermediate position will cause work to beychucked. Further movement of the handle to the extreme left or 3rd position will cause the spindle to be clutched, and thereafter the spindle carrier indexes. Another spindle then reaches the loading position. Movement of the manual control `handle toward the right to the 2nd position will cause the spindle to be unclutched, and further movement of the control valve handle back to the extreme right, or "1st position, as shown in the drawings, will cause the work to be unchucked. Thus the cycle is completed.

It is often desirable in a machine of this character to permit a chuck in any position to be opened, for example so that a faulty piece oi' work may be removed. With that end in View We have provided means for rotating the distributor plug 308 from its normal position, as shown in the drawings, so as to place the various passages heretofore described into communication with the various cylinders.- For example, it will be clearA that with the holding or detent lug device 353 withdrawn to the position shown in Fig. 3, the handle 354 may be moved so as to rotate the distributor plug 308 to any'position desired, so as to cause the passages now in communication with a particular cylinder to be placed in communication with any of the other cylinders. In fact, if it were desired, the loading position of the machine could be almost instantly changed merely by shifting the distributor plug 308 to the appropriate position.

While we have disclosed many features of novelty having structural or functional utility, it is to be noted that we have disclosed only a pre ferred form and that many changes, modica tions, fadditions, and omissions may be made within the scope of the invention as defined in the appended claims.

We claim:

l. In a chucking machine, a rotatable spindle, a chuck carried thereby, a fluid pressure actuated means for actuating said chuck, means for driving said spindle, a clutch controlling the same, a fluid pressure actuated means for actuating said clutch, and a single valve for controlling the flow of pressure fluid for both said fluid pressure actuated means.

2. In a chucking machine, a frame, a rotatable spindle, a chuck carried thereby, fluid pressure actuated means for actuating said chuck, means for driving said spindle, a clutch controlling the same, a fluid pressure actuated means carried by said frame and positioned for coaction with said clutch, and a single valve for controlling both of said fluid pressure actuated means.

3. In a chucking machine, a rotatable spindle, a chuck carried thereby, fluid pressure actuated means for actuating said chuck, means for driving said spindle, a clutch for controlling said driving means, fluid pressure actuated means for actuating said clutch, meansfor conducting pressure fluid to both said fluid pressure actuated means, and a single valve movable to one position to control the flow of fluid pressure for said clutch actuating means and movable to another position to control said chuck fluid pressure actuated means.

4. In a chucking machine, a rotatable spindle, a chuck carried thereby, fluid pressure actuated means for actuating said chuck, means for driving said spindle, a clutch for controlling the same,

fluid pressure actuated means for actuating said clutch, and means controlled from a single point for controlling the flow of pressure fluid to said clutch actuating means for disengaging said clutch and for thereafter controlling the flow of pressure fluid to said chuck actuating means for opening said chuck.

5. In a chucking machine, a frame, a rotatable spindle, a chuck carried thereby, fluid pressure means for actuating said chuck, means for driving spaid spindle, a clutch for controlling the same, a fluid pressure cylinder carried by said frame, a piston therein, means forming a coacting means between said piston and clutch for actuating the latter by said piston, and fluid passage means through said cylinder and leading to said fluid pressure actuated means for said chuck for actuating the latter.

6. In a chucking machine, a rotatable spindle, a chuck carried thereby, fluid pressure actuated means for actuating said chuck, means for driving said spindle, a clutch for controlling the same, fluid pressure actuated means for actuating said clutch, and a single control means for first controlling the flow of fluid to one of said fluid pressure actuated means to actuate the same, and thereafter controlling the flow of pressure fluid to the other of said fluid pressure actuated means for actuating the latter.

7. In a chucking machine, a rotatable spindle, a chuck carried thereby, uid pressure actuated means for actuating said chuck, means for driving said spindle, a clutch for controlling the same, fluid pressure actuated means for actuating said clutch, and control means movable to one position for controlling the flow of fluid pressure to one of said uid pressure actuated means and movable to another position for controlling the flow of fluid pressure to the other of said iluid pressure actuated means, for the purpose described.

8. In a chucking machine, a spindle carrier, means for indexing the same from station to station, a plurality of rotatable spindles carried by said spindle carrier, means for driving said spindies, clutch means for connecting said driving means to each of said spindles, a chuck carried by each of said spindles, fluid pressure actuated means for actuating the chuck of each of said spindles in loading station, and a single control valve for controlling the flow of pressure fluid to each of said fluid pressure actuated means.

9. In a chucking machine, a frame, an indexible spindle carrier carried thereby, a plurality of rotatable spindles carried by said spindle carrier,

means for indexing said spindle carrier, a chuck carried by each of said spindles, fluid pressure actuated chucking means carried by each of said spindles for actuating the chucks thereof, means for driving said spindles, a spindle clutch for clutching and unclutching each spindle from said vdriving means, fluid pressure actuated means cardexible spindle carrier thereon,l a plurality o! rotatable spindles carried by said spindle carrier, means for indexing saidv spindle carrier, a chuck carried by eachsaid spindle, means for driving said spindles, m'eans for disengaging each'said spindle from; lts driving means including'a duid .pressure actuated means, `a duid pressure actuated means tor actuating each o! said chucks in loading station, and a single control valve for controlling the dow voi' pressure duid to each of said duid4 pressure actuated means. for the purpose described.

11. In a chucking machine. a ira'me, an indexible spindle carrier thereon, a plurality of rotatable spindles carried by said spindle carrier, means for driving said' spindles, duid pressure actuated means for disengaging each of said spindles from said'driving means, a\chuck carried by each spindle, duid pressure actuated means for actuating said chucks, and a single valve movable to one position to control the dow "ated piston for actuating said yspindle drive disengaging means, a duid pressure operated piston for actuating the chuck ot each said spindle" when in loading station, and a single duid pressure control means for controlling the dow of duid pressure to said two duid pressure means.

13. In a machine -oi' the character indicated, a frame, an indexible spindle carrier thereon, a plurality of rotatable spindles carried by said spindle carrier, a. chuck carried by each said spindle, driving mea's'for said spindles, means i'or disengaging eachvot said spindles from its driving means including a slide mounted on said frame, a iluid pressure piston and cylinder for moving said slide i'or engins and disengaging said driving means with at least one of said spindles, duid pressure actuated means for actuating said chucks, duid passage means including controllingthe dow of duid pressure Vi'or disengaging said spindle from its drive means and movable to another position to open said chuck while said spindle is disengaged and movable to another position to cause said chuck to close and movable to another position to cause said spindle to again engage with its drive means.

15. In a chucking machine, a rotatable spindle, a chuck carried thereby, a duid pressure cylinder and piston for actuating said chuck, said cylinder being normally rotatable relatively to said spindle and being rotatably carried by the rear end thereof, valve means for controlling the dow of pressure duid to and from said cylinder, and means i'or starting and stopping rotation oi said spindle,

GEORGE O. GRIDLEY. DONALD H. MONTGOMERY. EARL H. WHEELER. 

